CN105485990A - Screw compressor drive control - Google Patents
Screw compressor drive control Download PDFInfo
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- CN105485990A CN105485990A CN201510982785.1A CN201510982785A CN105485990A CN 105485990 A CN105485990 A CN 105485990A CN 201510982785 A CN201510982785 A CN 201510982785A CN 105485990 A CN105485990 A CN 105485990A
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- 238000005057 refrigeration Methods 0.000 claims abstract description 22
- 238000000034 method Methods 0.000 claims abstract description 17
- 239000012530 fluid Substances 0.000 claims description 40
- 230000008859 change Effects 0.000 claims description 9
- 230000000712 assembly Effects 0.000 claims 6
- 238000000429 assembly Methods 0.000 claims 6
- 230000008878 coupling Effects 0.000 claims 4
- 238000010168 coupling process Methods 0.000 claims 4
- 238000005859 coupling reaction Methods 0.000 claims 4
- 239000007788 liquid Substances 0.000 description 11
- 230000004044 response Effects 0.000 description 11
- 238000005516 engineering process Methods 0.000 description 8
- 230000001133 acceleration Effects 0.000 description 5
- 238000007599 discharging Methods 0.000 description 4
- 230000006835 compression Effects 0.000 description 3
- 238000007906 compression Methods 0.000 description 3
- 208000028659 discharge Diseases 0.000 description 3
- 238000002474 experimental method Methods 0.000 description 3
- 230000005540 biological transmission Effects 0.000 description 2
- 239000012809 cooling fluid Substances 0.000 description 2
- 239000000110 cooling liquid Substances 0.000 description 2
- 230000002349 favourable effect Effects 0.000 description 2
- 230000006870 function Effects 0.000 description 2
- 230000017525 heat dissipation Effects 0.000 description 2
- 239000000203 mixture Substances 0.000 description 2
- 230000009467 reduction Effects 0.000 description 2
- 229920006395 saturated elastomer Polymers 0.000 description 2
- 239000011555 saturated liquid Substances 0.000 description 2
- 230000009466 transformation Effects 0.000 description 2
- 241000396377 Tranes Species 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 230000005494 condensation Effects 0.000 description 1
- 238000009833 condensation Methods 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000003993 interaction Effects 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 230000003287 optical effect Effects 0.000 description 1
- 239000003507 refrigerant Substances 0.000 description 1
- 230000001360 synchronised effect Effects 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
- F25B49/022—Compressor control arrangements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
- F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
- F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/06—Control using electricity
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
- F04C28/08—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by varying the rotational speed
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
- F25B1/047—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type of screw type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
- F25B49/025—Motor control arrangements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/40—Electric motor
- F04C2240/403—Electric motor with inverter for speed control
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/80—Other components
- F04C2240/81—Sensor, e.g. electronic sensor for control or monitoring
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2270/00—Control; Monitoring or safety arrangements
- F04C2270/03—Torque
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/02—Compressor control
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/02—Compressor control
- F25B2600/025—Compressor control by controlling speed
- F25B2600/0253—Compressor control by controlling speed with variable speed
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
An embodiment of method used to control operation of a screw compressor of a refrigeration system may include receiving status signals regarding operation of the screw compressor of the refrigeration system. The method may further include determining an operating point of the screw compressor based upon the received status signals, and selecting a torque profile for the screw compressor based upon the operating point. The method may also include driving the screw compressor per the selected torque profile. Refrigeration systems and compressor systems suitable for implementing the method are also presented.
Description
The application is that application people is Trane International Limited, international filing date is on August 18th, 2010, application number is 201080037055.X (international application no is PCT/US2010/045838), is entitled as the divisional application of the PCT application for a patent for invention of " drived control of screw compressor ".
Background technology
The pressure of cold-producing medium is elevated to condenser pressure from evaporator pressure by the compressor in refrigeration system.Evaporator pressure is sometimes referred to as suction pressure, and condenser pressure is sometimes referred to as discharge pressure.Under discharge pressure, cold-producing medium can cool required medium.The polytype compressor comprising rotary screw compressor is used in these refrigeration systems.
Screw compressor comprises towards the inhalation port of work chamber's opening of screw compressor and discharge port.Work chamber comprises the screw rotors of pair of meshing, and this limits compressed bag to the screw rotors of engagement between screw rotors and the inwall of work chamber.Receive cold-producing medium by inhalation port and cold-producing medium is delivered to compressed bag.The rotation of rotor closes compressed bag from inhalation port and is moved towards discharge port by cold-producing medium along with rotor and reduce the volume of compressed bag.Due to the reduction of compressed bag volume, cold-producing medium is delivered to discharge port with the discharge pressure being greater than suction pressure by rotor.
Summary of the invention
Disclose the embodiment of the method for the screw compressor of this system of refrigeration system, compressor assembly and control.The embodiment controlling the method for the operation of the screw compressor of refrigeration system can comprise the status signal received about the operation of the screw compressor of refrigeration system.The method also comprises the operating point based on received status signal determination screw compressor, and is that screw compressor selects torque curve based on this operating point.The method also can comprise according to selected torque curve drive screw formula compressor.Also proposed the refrigeration system of each embodiment, each embodiment of compressor assembly that are suitable for the operation implementing the control screw compressor disclosed.
Those skilled in the art can understand the advantage of the various embodiments described above and advantageous characteristic feature and other importance thereof reading following detailed description postscript by reference to the accompanying drawings.
Accompanying drawing explanation
By means of example and by accompanying drawing restriction, each embodiment is described at this.In order to simply and be clearly described, shown in accompanying drawing, component is not necessarily drawn in proportion.Such as, in order to clear, the size of some component may be amplified relative to other component.In addition, when thinking fit, corresponding or similar component is indicated with the Reference numeral repeated in the drawings and in which.
Fig. 1 illustrates the embodiment of the refrigeration system comprising compressor assembly.
Fig. 2 illustrates other details of the compressor assembly of Fig. 1.
Fig. 3 illustrates the flow chart of the control method that the compressor assembly of Fig. 1 performs.
Detailed description of the invention
Following description describes the technology of the compressor of refrigeration system, compressor assembly and these systems of control.In the following description, many details have been set forth so that provide the thorough understanding to described system and technology.But those skilled in the art can easily understand, these details can be there is no to put into practice each embodiment of described system and technology.In other cases, be not shown specifically and describe each concrete aspect of described system and technology, thus make described system and technology clearer.
Mention " embodiment ", " embodiment ", " exemplary embodiment " etc. in description, represent that described embodiment can comprise specific features, structure or characteristic, but each embodiment not necessarily comprises this specific features, structure or characteristic.In addition, these phrases not necessarily refer to same embodiment.Whether, when describing special characteristic, structure and characteristics in conjunction with an embodiment, other embodiment can comprise or otherwise implement these features, structure and characteristics, no matter clearly describe.
Can hardware, firmware, software or its combination in implement described system and technology some in.Some aspect of described system also can be embodied as storage instruction on a machine-readable medium, and these instructions can be read by one or more processor and be performed.Machine readable media can comprise any storage device that can store information with machine (such as calculation element) readable form.Such as, machine readable media can comprise read-only storage (ROM), random access storage device (RAM), magnetic disk storage medium, optical storage media, flash memory device and other medium.
Referring now to Fig. 1, an embodiment of refrigeration system 100 is shown.Refrigeration system 100 can make the fluid 110 of such as liquid refrigerant circulate to cool the space of such as room, house or building and so on.Circulation of fluid 110 can from the Spatial absorptive that will cool and remove heat and can subsequently by heat dissipation to it.As shown in the figure, refrigeration system 100 can comprise compressor assembly 120, condenser 130, expansion valve 140 and evaporimeter 150, condenser 130 is attached to condenser system 120, and expansion valve 140 is attached to condenser 130, and evaporimeter 150 is connected between compressor assembly 120 and expansion valve 140.
Compressor assembly 120 can comprise inhalation port 122 and discharge port 124.The inhalation port 122 of compressor assembly 120 can receive the fluid 110 being in the thermodynamic state being called saturated vapor.Along with fluid 110 is sent to discharge port 124 from inhalation port 122 by compressor assembly 120, compressor assembly 120 compressible fluid 110.Specifically, inhalation port 122 can receive the fluid 110 be under suction pressure and inlet temperature.Compressor assembly 120 compressible fluid 110 also can discharge compressed fluid 110 via discharge port 124 under higher than the discharge pressure of suction pressure.Compressing fluid 110 also to cause fluid 110 to be discharged under higher than the discharge temperature of inlet temperature.The fluid 110 of discharging from discharge port 124 can be in the thermodynamic state being called superheated steam.Thus, the fluid 110 of discharging from compressor assembly 120 can be in fluid 110 can be easy to carry out the temperature and pressure of condensation with cooling-air or cooling fluid.
Condenser 130 can be attached to the discharge port 124 of compressor assembly 120 to receive fluid 110.When fluid 110 is through condenser 130, condenser 130 meeting cooling fluid 110, and fluid 110 can be transformed into saturated liquid from superheated steam.For this reason, condenser 130 can comprise coil pipe or pipeline, and fluid 110 is through these coil pipes or pipeline, and cooling-air or cooling liquid cross these coil pipes or Flows.Owing to passing through cooling-air or the cooling liquid of the coil pipe of condenser 130, heat can discharge from refrigeration system 100 or otherwise be delivered to air or liquid by fluid 110, and heat is taken away again by air or liquid.
Expansion valve 140 can receive from condenser 130 fluid 110 being in the thermodynamic state being called saturated liquid.Expansion valve 140 can reduce rapidly the pressure of fluid 110.Pressure reduces the adiabatic flash at least partially that can cause fluid 110 rapidly, and this can reduce the temperature of fluid 110.Specifically, adiabatic flash can produce the gas-liquid mixture of fluid 110, and the temperature of the gas-liquid mixture of this fluid 110 is lower than the temperature in the space that will cool.
Evaporimeter 150 can receive cold fluid 110 from expansion valve 140, and cold fluid 110 can be directed across coil pipe or the pipeline of evaporimeter 150.Warm air or liquid can cross coil pipe or the piping loop of evaporimeter 150 from the space that will cool.Passing through the coil pipe of evaporimeter 150 or the warm air of pipeline or liquid can make the liquid part of cold fluid 110 evaporate.Meanwhile, the warm air or the liquid that pass through coil pipe or pipeline can be cooled by fluid 110, therefore reduce want the temperature of cooling space.Fluid 110 can be delivered to the inhalation port 122 of compressor assembly 120 by evaporimeter 150 as saturated vapor.Therefore, evaporimeter 150 can complete kind of refrigeration cycle and fluid 110 can be back to compressor assembly 120, again to cycle through compressor assembly 120, condenser 130 and expansion valve 140.Therefore, in refrigeration system 100, evaporimeter 150 can from the Spatial absorptive that will cool and remove heat, and condenser 130 can subsequently by absorbed heat dissipation to air or liquid, heat is taken away from the space that will cool by air or liquid.
Referring now to Fig. 2, other details of the embodiment about compressor assembly 120 is shown.Specifically, shown compressor assembly 120 can comprise controller 210, memory 220, electric motor system 230 and screw compressor 240.Compressor assembly 120 also can comprise one or more electric transducer 250, torque sensor 255, suction pressure and/or temperature sensor 260 and discharge pressure and/or temperature sensor 270.Sensor 250,255,260,270 value of the operation of instruction screw compressor 240 provides status signal 290.
Controller 210 can comprise cooperation to control the processor of operation of screw compressor 240, microcontroller, analog circuit, digital circuit, firmware and/or software.Memory 220 can comprise Nonvolatile memory device and store torque curve 222 array for screw compressor 240 in a permanent fashion, and Nonvolatile memory device is flash memory device, read-only storage (ROM) device, electric erasable/programming ROM device and/or battery powered random access storage device (RAM) device such as.Memory 220 also can comprise the instruction that controller 210 can perform the operation controlling screw compressor 240.
As being hereafter explained in more detail, controller 210 can from one or more sensors 250,255,260,270 accepting state signal 290 of compressor assembly 120, and status signal 290 provides the information of the operation about screw compressor 240.Based on status signal 290, controller 210 can determine operational mode and/or the operating point of screw compressor 240, and can produce based on determined operational mode and/or operating point the operation that one or more command signal 212 carrys out adjusting screw(rod) formula compressor 240.Specifically, the controller 210 in an embodiment can be selected torque curve 222 based on the operational mode determined from status signal 290 and/or operating point from the array of torque curve 222 or otherwise can determine the torque curve 222 of screw compressor 240.Then controller 210 can produce command signal 212 according to the torque curve 222 obtained from screw compressor 240, and this command signal 212 requires that torque 238 is transported to screw compressor 240 by electric motor system 230.
Electric motor system 230 can in response to the command signal 212 drive screw formula compressor 240 received from controller 210.Specifically, electric motor system 230 can comprise variable frequency drives 232 and motor 234.Motor 234 can be attached to screw compressor 240 with the screw rotors 242,244 of the engagement of drive screw formula compressor 240.In one embodiment, motor 234 can comprise permanent magnet motor, and this permanent magnet motor is to depend on the speed of the frequency of multi-phase controlling signal 236 and to depend on that the torque 238 of the electric current supplied by multi-phase controlling signal 236 drives rotor 242,244.As shown in the figure, variable frequency drives 232 can receive command signal 212 from controller 210 and can produce multi-phase controlling signal 236.Specifically, variable frequency drives 232 can regulate frequency and the electric current of multi-phase controlling signal 236 based on the command signal received from controller 210.As mentioned above, controller 210 can produce command signal 212 according to the torque curve 222 selected for screw compressor 240.Like this, variable frequency drives 232 in response to command signal 212 according to the frequency of the torque curve 222 regulable control signal 236 selected for screw compressor 240 and electric current.
As shown in the figure, electric transducer 250 can locate electric operation characteristic with motor sensor 234 near motor 234.Electric transducer 250 value of electric operation characteristic that also available instruction senses provides status signal 290.In one embodiment, electric transducer 250 can comprise one or more current sensor.Current sensor can be positioned to sense the status signal 290 that also can be produced instruction institute current sensor by control signal 236 to the electric current that motor 234 supplies.In one embodiment, the electric current supplied by control signal 236 is depended in the torque 238 produced by motor 234.Thus, the status signal 290 being supplied to the electric current of motor 234 is indicated also can to indicate the torque 238 supplied by motor 234.Although the electric transducer 250 in an embodiment comprises the current sensor that sensing is supplied to the electric current of motor 234, but electric transducer 250 also can other electric operation characteristic of motor sensor 234, the input of such as motor 234 and/or the voltage at other parts place, electric current, phase angle, effective impedance, and provide instruction sense the status signal 290 of electric operation characteristic.
As shown in the figure, torque sensor 255 can locate to sense the torque 238 applied to screw compressor 240 by electric motor system 230 near electric motor system 230.Torque sensor 255 value of torque 238 that also available instruction senses provides status signal 290.In one embodiment, torque sensor 255 can comprise the one or more torsion members be positioned between motor 234 and compressor 240.Then torque sensor 255 can produce instruction was sensed and/or be applied to the torque 238 of torsion member status signal 290 by torsion member.
Screw compressor 240 also can comprise inhalation port 122 and the discharge port 124 of compressor assembly 120.As shown in the figure, suction pressure and/or temperature sensor 260 can be positioned near the inhalation port 122 of screw compressor 240, to sense pressure and/or the temperature of the fluid 110 entering inhalation port 122.Equally, discharge pressure and/or temperature sensor 270 can be positioned near the discharge port 124 of screw compressor 240, to sense pressure and/or the temperature of the fluid 110 of discharging from discharge port 124.In addition, suction pressure and/or temperature sensor 260 can provide status signal 290 with indicating the pressure of fluid 110 entering inhalation port 122 that sense and/or the value of temperature, and discharge pressure and/or temperature sensor 270 pressure of fluid 110 of discharging from discharge port 124 that can sense with instruction and/or the value of temperature provide status signal 290.
Screw compressor 240 also can comprise the screw rotors 242,244 of multiple engagement.The screw rotors 242,244 of multiple engagement can limit one or more compressed bag between screw rotors 242,244 and the inner chamber wall of screw compressor 240.The torque 238 supplied by motor 234 can make screw rotors 242,244 rotate, and therefore closes compressed bag from inhalation port 122.Fluid 110 also moves towards discharge port 124 along with rotor 242,244 and reduces the volume of compressed bag further by the rotation of screw rotors 242,244.Owing to reducing the volume of compressed bag, screw rotors 242,244 by fluid 110 under higher than the discharge pressure of suction pressure with higher than the discharge temperature of inlet temperature under be delivered to discharge port 124.
The operation of screw compressor 240 when compression and mobile fluid 110 produces axis and radial load.The interaction of screw rotors 242,244, axial force and radial load may cause the power of change and uneven rotor motion and the end surfaces to chamber wall, bearing and screw compressor 240 in time.The chamber wall that lubricating oil is screw compressor 240, rotor 242,244 and bearing provide buffer film, but do not prevent from changing in time and the transmission of uneven axis and radial load.When selecting torque curve 222 for screw compressor 240, the torque curve 222 of the mode drive screw formula compressor 240 selected to reduce unproductive radial load and axial force attempted by controller 210.
Different screw compressor designs presents operation characteristic and some common operation characteristic of some uniqueness usually.The roughly common operation characteristic of many screw compressor designs is that the design of multiple screw compressor presents the fluctuating torque consistent with the suction of screw compressor, compression and discharge stage.Other roughly common operation characteristic comprises power from positive screw rotors to the dynamic transmission of female screw formula rotor of engagement and the axial thrust of screw rotors 242,244.
Due to unique operation characteristic that different screw compressor designs, experiment can be carried out to various torque curve 222 to determine, to identify the favourable torque curve 222 for the operating point place of screw compressor design in different operational mode and/or in these operational modes.Specifically, screw compressor 222 can run at friction speed, average rotor electric current, discharge pressure and/or temperature, suction pressure and/or temperature and/or other operational factor, to obtain for the favourable torque curve 222 of screw compressor 240 at various operational mode and/or operating point.Such as, screw compressor 240 can run to obtain detent torque curve 222, run to obtain accelerating torque curve 222 and run to obtain deceleration curve 222 under deceleration mode in turbo mode in the startup mode.
Based on this experiment, the array of the transformation curve 222 being used for relevant each operational mode and/or each operating point can be set up to screw compressor 240.In one embodiment, every bar torque curve of the array of transformation curve 222 is included in the figure of motor to the torque value of compressor shaft of generation during rotor once or several times rotates.This figure can be repetition and can define, because once rotating of motor may not be equal to compressor by the once rotation driving rotor 242,244 once above complete motor rotary course.The length of torque curve 222 may be defined as the integer that torque figure is repeated successively and rotates.Controller 210 can repeatedly select and/or application of torque curve 222 to realize required control result.
In addition, in order to keep required extent of stability, the array of torque curve 222 can be built, and can by controller 210 with each torque curve 222 of the way selection of the stability contorting function realizing screw compressor 240.Specifically, the array of torque curve 222 can be built into the speed of torque-limiting 238 change with the stability of retentive control function.In one embodiment, by forming the array of torque curve 222 to keep stability with the torque curve 222 of the roughly equal rate of change of maintenance.This determines the operating condition of screw compressor 240 by experiment under unequal operating point difference and torque curve difference in the array of torque curve 222 is remained on roughly equal value to realize.
In one embodiment, torque curve 222 can be built into and represent directly as the torque control value of sampled point about the time.In another embodiment, torque curve 222 can be built into the torque value represented as the integer harmonics multiple of the main running frequency of screw compressor 240.Specifically, the harmonic wave defining torque curve 222 can be expressed according to harmonic frequency amplitude and phase place.
Referring now to Fig. 3, an embodiment of the control method can implemented by controller 210 is shown.Controller 210 in one embodiment periodically performs the control method of Fig. 3 with the torque curve 222 of adjustment for drive screw formula compressor 240.At square frame 305 place, controller 210 can from each sensor 250,255,260,270 accepting state signal 290 of compressor assembly 120, and these status signals 290 provide the information of the current operation about screw compressor 240.The controller 210 at square frame 310 place can determine whether screw compressor 240 is in start-up mode.Controller 210 can determine based on the data provided by status signal 290 whether screw compressor 240 is in start-up mode.Based on other data of refrigeration system 100, controller 210 can determine whether screw compressor 240 is in start-up mode.Such as, controller 210 can will be enabled refrigeration system 100 in response to the indicating controller 210 from control panel or temperature-adjusting device (not shown) and starts the signal of screw compressor 240 and determine that screw compressor 240 is in start-up mode.In response to determining that screw compressor 240 is in start-up mode, at square frame 315 place, controller 210 can select detent torque curve 222 from memory 220.
In response to determining that screw compressor 240 is not in start-up mode, at square frame 320 place, controller 210 can determine that whether screw compressor 240 is in acceleration.Specifically, controller 210 can determine that based on status signal 290 whether the rotating speed of the rotor 242,244 engaged is in increase.In one embodiment, controller 210 based on status signal 290 several sampled point and accelerate threshold value and determine that whether screw compressor 240 is in acceleration, the acceleration of rotor 242,244 can not be wrongly interpreted as with the minor fluctuations of the rotating speed of the rotor 242,244 engaged during guaranteeing stable or steady-state operation.In response to determining that screw compressor 240 accelerates, at square frame 325 place, controller 210 can select accelerating torque curve 222 from memory 220.
In response to determining screw compressor 240 not in acceleration, at square frame 330 place, controller 210 can determine that whether screw compressor 240 is in deceleration.Specifically, controller 210 can determine that based on status signal 290 whether the rotating speed of the rotor 242,244 engaged is in reduction.In one embodiment, based on several sampled point of status signal 290 and deceleration threshold value, controller 210 determines that whether screw compressor 240 is in deceleration, can not be wrongly interpreted as the deceleration of rotor 242,244 with the minor fluctuations of the rotating speed of the rotor 242,244 engaged during guaranteeing stable or steady-state operation.In response to determining that screw compressor 240 slows down, at square frame 335 place, controller 210 can select deceleration torque curve 222 from memory 220.
In response to determining screw compressor 240 not in deceleration, at square frame 340 place, controller 210 can confirm the relatively stable or stable state of the operation of screw compressor 240.At refrigeration system 100 run duration, screw compressor 240 can experience the period that is relatively stable or steady-state operation, at the rotating speed relative constancy of this period internal rotor 242,244, suction pressure and/or temperature relative constancy, and discharge pressure and/or temperature relative constancy.Thus, at square frame 340 place, based on status signal 290, controller 210 can determine whether screw compressor 240 runs at operating point place that is relatively stable or stable state.Be similar to above acceleration and deceleration is determined, whether controller 210 can run at relatively stable or steady state point based on several sampled point of status signal 290 and each threshold value determination screw compressor 240, thus guarantees that the minor fluctuations of rotating speed, suction pressure and/or temperature and/or discharge pressure and/or temperature can not determine that screw compressor 240 does not run at operating point that is relatively stable or stable state mistakenly.In response to determining the not relatively stable or stable state of the operation of screw compressor 240, at 345 places, controller 210 is that screw compressor 240 selects acquiescence torque curve 222, this make not to start, accelerate, to slow down and/or period electric motor system 230 that stable operation is relevant provides suitable torque 238 for screw compressor 240.
In response to determining that the operation of screw compressor 240 is relatively stable, at square frame 350 place, controller 210 can determine the operating point of screw compressor 240 based on status signal 290.As mentioned above, the array of torque curve 222 is included in the torque curve 222 for screw compressor 240 at the various speed of service, suction pressure and/or temperature and discharge pressure and/or temperature.Therefore, at square frame 355 place, controller 210 can select to correspond to based on status signal 290 torque curve 222 of the speed of service, suction pressure and/or temperature indicated by status signal 290 and discharge pressure and/or temperature from memory 220.In other each embodiment, multiple torque curves 222 that controller 210 can be selected near the operating point that indicates at status signal 290 from memory 220, and by carrying out interpolation method from the torque curve 222 selected and produce the torque curve 222 of the screw compressor 240 for running at indicated operating point.
At square frame 360 place, controller 210 can produce command signal 212 according to the torque curve 222 selected for screw compressor 240, and this command signal 212 requires that torque 238 is fed to screw compressor 240 by electric motor system 230.As mentioned above, screw compressor 240 presents fluctuating torque due to rotor 242,244 reception, compression and displacement fluids 110 usually.Torque curve 222 in one embodiment can be built into the fluctuating torque presented with screw compressor 240 and mate.Thus, when switching to another torque curve 222 from a torque curve 222, this switching ideally timing is consistent with torque ripple.Synchronously this in order to realize, controller 210 produces command signal 212, makes electric motor system 230 realize the switching of the torque curve 222 synchronous with the fluctuating torque of screw compressor 240.In other embodiments, other technology can be used realize synchronously.Such as, electric motor system 230 can sense torque ripple and in due course between switch torque curve 222.
The inspiration being subject to above-mentioned instruction can carry out multiple change and change to disclosed each embodiment.Therefore, should be appreciated that within the scope of appended claims, disclose each embodiment each side can put into practice from above-mentioned different mode.
Claims (16)
1. control a method for the operation of the compressor of refrigeration system, described method comprises:
Receive the status signal of the fluctuating torque produced about one or more rotors of described compressor;
The operating point of described compressor is determined based on received status signal;
Be described compressor determination torque curve based on described operating point, wherein determined torque curve represents the change being applied to the torque of described compressor during the rotation of described one or more rotor of described compressor; And
The torque of described compressor is applied to according to determined torque curve adjustment.
2. the method for claim 1, is characterized in that, describedly determines to comprise the torque curve obtained for determined torque curve, the fluctuating torque that the described one or more rotor of determined torque curve coupling produces.
3. the method for claim 1, is characterized in that, described adjustment comprises the switching timing of determined torque curve for consistent with the torque ripple of the fluctuating torque that described one or more rotor produces.
4. the method for claim 1, is characterized in that, describedly determines to comprise:
One or more torque curve is selected based on described operating point; And
From the torque curve of described one or more selection, interpolation goes out determined torque curve.
5., for a control system for the motor and compressor that control refrigeration system, comprising:
Memory, described memory has the torque curve of multiple storage for described compressor; And
Controller, described controller is configured to: (a) receives the status signal of the fluctuating torque produced about one or more rotors of described compressor; B () determines the operating point of described compressor based on received status signal; C () is described compressor determination torque curve based on the torque curve of described operating point and described multiple storage, wherein determined torque curve represents the change being applied to the torque of described compressor during the rotation of described one or more rotor of described compressor; And (d) produces one or more control signal according to determined torque curve, described control signal is applied to the torque of described compressor by described motor according to determined torque curve adjustment.
6. control system as claimed in claim 5, is characterized in that, described controller is also configured to obtain the torque curve for determined torque curve, the fluctuating torque that the described one or more rotor of determined torque curve coupling produces.
7. control system as claimed in claim 5, it is characterized in that, described controller is also configured to the switching timing of determined torque curve as consistent with the torque ripple of the fluctuating torque that described one or more rotor produces.
8. control system as claimed in claim 5, it is characterized in that, described controller is also configured to:
One or more torque curve is selected based on described operating point; And
From the torque curve of described one or more selection, interpolation goes out determined torque curve.
9. a compressor assembly, comprising:
Compressor, described compressor comprises the one or more rotors being configured to compressed fluid;
Controller, described controller: the status signal of the fluctuating torque that one or more rotors that (a) receives the described compressor of instruction produce; B () is based on the described operating point determination torque curve of described compressor; And (c) generation requires that torque is sent to the command signal of described compressor according to determined torque curve; And
Electric motor system, described electric motor system is configured to receive described command signal from described controller, and change according to the determined torque curve that the command signal of described reception requires the torque being sent to described compressor, wherein determined torque curve represents that the torque during described electric motor system rotates between described electric motor system and described compressor changes.
10. compressor assembly as claimed in claim 9, is characterized in that, described controller is also configured to obtain the torque curve for determined torque curve, the fluctuating torque that the described one or more rotor of determined torque curve coupling produces.
11. compressor assemblies as claimed in claim 9, is characterized in that, described controller is also configured to the switching timing of determined torque curve as consistent with the torque ripple of the fluctuating torque that described one or more rotor produces.
12. compressor assemblies as claimed in claim 9, it is characterized in that, described controller is also configured to:
One or more torque curve is selected based on described operating point; And
From the torque curve of described one or more selection, interpolation goes out determined torque curve.
13. 1 kinds of compressor assemblies, comprising:
Compressor, described compressor comprises the one or more rotors being configured to compressed fluid;
Motor, described motor reception control signal and drive described one or more rotor according to the control signal that receives;
Controller, the status signal of the fluctuating torque that described one or more rotor that described controller receives the described compressor of instruction produces, based on the described operating point determination torque curve of described compressor, and generation requires that described motor is according to the driven command signal of determined torque curve; And
Variable frequency drives, described variable frequency drives receives described command signal and produces the control signal of the torque changed between described motor and described compressor according to determined torque curve, and wherein determined torque curve represents the torque change during described motor rotates between described motor and described compressor.
14. compressor assemblies as claimed in claim 13, is characterized in that, described controller is also configured to obtain the torque curve for determined torque curve, the fluctuating torque that the described one or more rotor of determined torque curve coupling produces.
15. compressor assemblies as claimed in claim 13, is characterized in that, described controller is also configured to the switching timing of determined torque curve as consistent with the torque ripple of the fluctuating torque that described one or more rotor produces.
16. compressor assemblies as claimed in claim 13, it is characterized in that, described controller is also configured to:
One or more torque curve is selected based on described operating point; And
From the torque curve of described one or more selection, interpolation goes out determined torque curve.
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| US12/544,582 US8365544B2 (en) | 2009-08-20 | 2009-08-20 | Screw compressor drive control |
| US12/544,582 | 2009-08-20 | ||
| CN201080037055.XA CN102822528B (en) | 2009-08-20 | 2010-08-18 | The drived control of screw compressor |
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| CN201080037055.XA Division CN102822528B (en) | 2009-08-20 | 2010-08-18 | The drived control of screw compressor |
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| CN105485990A true CN105485990A (en) | 2016-04-13 |
| CN105485990B CN105485990B (en) | 2019-04-30 |
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| CN201080037055.XA Active CN102822528B (en) | 2009-08-20 | 2010-08-18 | The drived control of screw compressor |
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| EP (2) | EP3269982B1 (en) |
| CN (2) | CN105485990B (en) |
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Also Published As
| Publication number | Publication date |
|---|---|
| US20170343261A1 (en) | 2017-11-30 |
| US10352608B2 (en) | 2019-07-16 |
| US20150052921A1 (en) | 2015-02-26 |
| EP3269982A1 (en) | 2018-01-17 |
| CN105485990B (en) | 2019-04-30 |
| EP2467604B1 (en) | 2017-08-16 |
| CN102822528A (en) | 2012-12-12 |
| CA2768560A1 (en) | 2011-02-24 |
| EP3269982B1 (en) | 2019-04-10 |
| US20130145787A1 (en) | 2013-06-13 |
| CN102822528B (en) | 2016-01-20 |
| US9733002B2 (en) | 2017-08-15 |
| US8875530B2 (en) | 2014-11-04 |
| US20110041533A1 (en) | 2011-02-24 |
| US8365544B2 (en) | 2013-02-05 |
| EP2467604A2 (en) | 2012-06-27 |
| WO2011022455A3 (en) | 2013-10-03 |
| WO2011022455A2 (en) | 2011-02-24 |
| CA2768560C (en) | 2016-03-22 |
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